CN211900987U

CN211900987U - Exhaust pipe of compressor and compressor

Info

Publication number: CN211900987U
Application number: CN202020403548.1U
Authority: CN
Inventors: 耿樵; 刘鹏; 张霞
Original assignee: Shanghai Highly Electrical Appliances Co Ltd
Current assignee: Shanghai Highly Electrical Appliances Co Ltd
Priority date: 2020-03-25
Filing date: 2020-03-25
Publication date: 2020-11-10
Anticipated expiration: 2030-03-25

Abstract

The utility model provides an exhaust pipe of a compressor and a compressor, wherein the exhaust pipe is communicated with a shell of the compressor through an oil equalizing pipe, the exhaust pipe passes through an upper shell cover to be communicated with the inside of the shell, the exhaust pipe is provided with a first end part positioned in the shell and a second end part positioned outside the shell, and the inner diameter of the first end part is larger than that of the second end part; the application reduces the oil yield of the rotor type compressor, not only ensures the operational reliability of the compressor, but also promotes the performance of the compressor.

Description

Exhaust pipe of compressor and compressor

Technical Field

The utility model relates to a compressor technical field, specifically speaking relates to an blast pipe and compressor of compressor.

Background

The existing multi-split air conditioner technology is fast in development and more widely applied. In order to solve the problem of oil balance in a plurality of compressors adopting a multi-split technology, an oil equalizing pipe is arranged on each compressor. Referring to fig. 1, the oil equalizing pipe 102 communicates the casing 103 of the compressor and the discharge pipe 101, and the discharge pipe 101 penetrates the upper casing cover of the compressor to communicate with the inside of the casing 103. Since the compressor needs to be connected to the air conditioning system pipeline, there is a problem of pipeline vibration after the air conditioning system pipeline is connected.

To improve this problem, the inner diameter of the discharge pipe 101 of the compressor in the prior art is generally designed to be small. After the inner diameter of the exhaust pipe 101 is decreased, the flow rate of the gaseous refrigerant flowing through the exhaust pipe 101 from the equalizing pipe 102 is increased, which increases the pressure difference between both ends of the equalizing pipe 102. When the pressure difference increases, the flow rate of the refrigerant is further increased. During the outflow of the gaseous refrigerant, a small amount of lubricating oil flows out along with the gaseous refrigerant. The more refrigerant flows out of the compressor through the oil equalizing pipe 102, the more lubricating oil mixed in the gaseous refrigerant flows out, the higher oil output rate of the compressor is caused, the problem of lubricating oil shortage of the compressor is possibly caused, and the running reliability of the compressor is influenced. And, the performance of the compressor is also reduced after the pipe diameter of the exhaust pipe is reduced.

SUMMERY OF THE UTILITY MODEL

In view of this, the utility model provides an exhaust pipe and compressor of compressor reduces rotor compressor's the oil yield to under the prerequisite of guaranteeing compressor operational reliability, the performance of compressor has been promoted.

According to an aspect of the present invention, there is provided an exhaust pipe of a compressor, the exhaust pipe is communicated with a casing of the compressor through an oil equalizing pipe, and the exhaust pipe passes through an upper casing cover and is communicated with an inside of the casing, the exhaust pipe has a first end portion located in the casing and a second end portion located outside the casing, an inner diameter of the first end portion is greater than an inner diameter of the second end portion.

Preferably, the compressor has a displacement Q and the first end portion has an inner diameter D₁Said D is₁And Q satisfies D₁:Q>1/6。

Preferably, the exhaust pipe is provided with a flaring part, a transition part and an exhaust part in sequence along the direction departing from the shell; the inner diameter of the flared portion is equal to the inner diameter of the first end portion, and the inner diameter of the exhaust portion is equal to the inner diameter of the second end portion; the transition portion has an inner diameter that gradually decreases in a direction away from the housing.

Preferably, along the length extension direction of the exhaust pipe, the length of the exhaust pipe is L, and the length of the flared part is L₁Said L is₁And L satisfies 1/5<L₁:L<2/3。

Preferably, along the length extension direction of the exhaust pipe, the length of the exhaust pipe is L, and the length of the transition part is L₂Said L is₂And L satisfies L₂:L<1/10。

Preferably, along the length extension direction of the exhaust pipe, the length of the exhaust pipe is L, and the length of the exhaust part is L₃Said L is₃And L satisfies 1/4<L₃:L<2/3。

Preferably, the flared part is provided with an oil equalizing hole, and the oil equalizing pipe is communicated with the exhaust pipe through the oil equalizing hole.

Preferably, the inner diameter of the first end of the exhaust pipe ranges from [16.1mm, 25mm ].

Preferably, the exhaust pipe is tapered.

According to another aspect of the present invention, there is provided a compressor comprising the exhaust pipe of the compressor of any one of the above aspects.

Compared with the prior art, the utility model beneficial effect lie in:

the utility model provides an inside diameter of blast pipe and compressor of compressor through setting up the first end that the blast pipe is located the casing is greater than the inside diameter that the blast pipe is located the outer second end of casing, compare prior art when keeping the second end internal diameter unchangeable, the inside diameter of blast pipe first end has been increased, the sectional area of refrigerant circulation in the first end has been increased, the velocity of flow of gaseous state refrigerant has been reduced, and then the lubricating oil along with the refrigerant outflow has been reduced, rotor compressor's oil yield has been reduced, the operational reliability of compressor has not only been guaranteed, and the performance of compressor has been promoted.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the invention and together with the description, serve to explain the principles of the invention. It is obvious that the drawings in the following description are only some embodiments of the invention, and that for a person skilled in the art, other drawings can be derived from them without inventive effort.

FIG. 1 is a schematic view of a rotor compressor with an oil equalizing pipe in the housing according to the prior art;

FIG. 2 is a cross-sectional view of an exhaust pipe of the compressor of FIG. 1;

fig. 3 is a schematic structural diagram of an exhaust pipe of a compressor disclosed in an embodiment of the present invention;

FIG. 4 is a cross-sectional view of the exhaust pipe of FIG. 3;

fig. 5 is a schematic structural view of a discharge pipe of a compressor according to another embodiment of the disclosure.

Detailed Description

Example embodiments will now be described more fully with reference to the accompanying drawings. Example embodiments may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the concept of example embodiments to those skilled in the art. The described features, structures, or characteristics may be combined in any suitable manner in one or more embodiments. In the following description, numerous specific details are provided to give a thorough understanding of embodiments of the disclosure. One skilled in the relevant art will recognize, however, that the subject matter of the present disclosure can be practiced without one or more of the specific details, or with other methods, materials, devices, etc. In other instances, well-known technical solutions have not been shown or described in detail to avoid obscuring aspects of the present disclosure. The same reference numerals in the drawings denote the same or similar structures, and thus their detailed description will be omitted.

The terms "a," "an," "the," "said," and "at least one" are used to indicate the presence of one or more elements/components/parts/etc.; the terms "comprising," "having," and "providing" are intended to be inclusive and mean that there may be additional elements/components/etc. other than the listed elements/components/etc.

Fig. 1 is a schematic view of a rotor type compressor having an oil equalizing pipe 102 formed outside a casing according to the related art, and fig. 2 is a schematic sectional view of an exhaust pipe of the compressor of fig. 1. As shown in fig. 1 and 2, after the compressor is connected to the air conditioning system pipeline, in order to improve the vibration problem of the air conditioning system pipeline, the pipe diameter of the exhaust pipe 101 needs to be reduced. However, this results in a high flow rate of the gaseous refrigerant flowing through the discharge pipe 101, and further results in a large pressure difference across the oil equalizing pipe 102. On the other hand, the more refrigerant flowing out of the compressor through the oil equalizing pipe 102 causes the more lubricant oil mixed in the gaseous refrigerant to flow out, resulting in a higher oil discharge rate of the compressor.

Fig. 3 is a schematic structural diagram of a discharge pipe of the compressor disclosed in the present embodiment, and fig. 4 is a schematic sectional diagram of the discharge pipe in fig. 3. The exhaust pipe 101 in this embodiment is communicated with the casing 103 of the compressor through an oil equalizing pipe 102, and the exhaust pipe passes through the upper casing cover to be communicated with the inside of the casing 103. As shown in fig. 3 and 4, exhaust pipe 101 in the present embodiment has a first end portion 201 located inside casing 103 and a second end portion 202 located outside casing 103, and the inner diameter of first end portion 201 is larger than the inner diameter of second end portion 202. I.e., the end of discharge pipe 101 closer to compressor housing 103 has a larger inner diameter than the end farther from compressor housing 103.

That is, the present application keeps the inner diameter of the second end 202 unchanged, and at the same time, the inner diameter of the first end 201 of the exhaust pipe 101 is increased, the cross-sectional area of the first end 201 where the refrigerant flows is increased, the flow rate of the gaseous refrigerant is reduced, and then the lubricating oil flowing out along with the refrigerant is reduced, and the oil yield of the rotor compressor is reduced. And the inner diameter of the second end portion 202 connected to the air conditioning system pipe is not increased so that the vibration of the system pipe is not affected. On the other hand, when the refrigerant circulates in the exhaust pipe 101, the inner diameter of the exhaust pipe 101 gradually decreases in one section along the flowing direction of the refrigerant, so that certain resistance can be caused to the circulating gaseous refrigerant, the flow speed of the gaseous refrigerant is reduced, lubricating oil flowing out along with the refrigerant is reduced, and the oil yield of the compressor is reduced. After the flow rate of the gaseous refrigerant is reduced, the pressure difference between the two ends of the oil equalizing pipe 102 is also reduced, which is further beneficial to reducing the flow rate of the gaseous refrigerant and forming a positive feedback effect.

In this embodiment, the inner diameter of the first end of the exhaust pipe has a value range of [16.1mm, 25mm]. This is not limited by the present application. The compressor has a discharge capacity Q and the first end 201 has an inner diameter D₁D above₁And Q satisfies D₁:Q>1/6. The second end 202 has an inner diameter D₂，D₁>D₂. The rotor compressor under the displacement limitation has a more obvious improvement on the performance of the compressor by adopting the exhaust pipe 101.

In the present embodiment, the exhaust pipe 101 includes a flared portion 301, a transition portion 302, and an exhaust portion 303 in this order in a direction away from the housing 103. The flared portion 301 has an inner diameter equal to the inner diameter of the first end portion 201, and the exhaust portion 303 has an inner diameter equal to the inner diameter of the second end portion 202. The transition portion 302 has a gradually decreasing inner diameter in a direction away from the housing 103.

As shown in fig. 3 and 4, the flared portion 301 is provided with an oil equalizing hole 104, and the oil equalizing pipe 102 communicates with the exhaust pipe 101 through the oil equalizing hole 104. Since the length of the flared portion 301, if too long, affects the wall thickness of the flared portion 301, and thus the operational reliability of the compressor. If the length of the flared portion 301 is too short, the oil equalizing hole 104 is not easily opened. Therefore, along the longitudinal extension direction of the exhaust pipe 101, the length of the exhaust pipe 101 is L, and the length of the flared portion 301 is L₁In this embodiment, L is₁And L satisfies 1/5<L₁:L<2/3. For example, in one embodiment, L₁L can take the value of 0.25, 0.3, 0.35, 0.4, 0.45, 0.5, 0.55, 0.6 or 0.65, etc.

The flared portion 301 of the discharge pipe 101 disclosed in this embodiment increases the inner diameter of the end portion to reduce the flow velocity of the refrigerant, thereby reducing the pressure difference between the two ends of the oil equalizing pipe 102, and the reduction of the pressure difference is further beneficial to the reduction of the flow velocity of the refrigerant, so as to reduce the oil outlet rate of the compressor.

In a preferred embodiment, the inner diameter of the first end portion 201 of the exhaust pipe 101 in the prior art is [6mm, 16mm ], the inner diameter of the flared portion 301 in the present application is [16.1mm, 25mm ], and the inner diameter of the exhaust portion 303 is [6mm, 16mm ]. Compared with the prior art, the flow speed of the refrigerant flowing through the flared part 301 is reduced by increasing the inner diameter of the first end part 201, so that the pressure of the exhaust pipe 101 close to one side of the oil equalizing pipe 102 is increased under the condition that the pressure of the inside of the shell 103 close to one side of the oil equalizing pipe 102 is kept unchanged, and the pressure difference between the two ends of the oil equalizing pipe 102 is reduced. This further facilitates to reduce the flow rate of the refrigerant at the first end portion 201, thereby reducing the oil yield of the compressor and improving the performance of the compressor.

In the transition portion 302, if the transition portion 302 is too long, the difficulty of processing is high, the processing is not easy, and the lengths of the flared portion 301 and the exhaust portion 303 are also affected. Therefore, the transition portion 302 has a length L₂Then L in this embodiment₂And L satisfies L₂:L<1/10. In one embodiment, L₂L can take the value of 0.02, 0.04, 0.06 or 0.08, etc. The transition portion 302 is arranged to reduce the cross-sectional area of gas flowing through the gas exhaust pipe 101 in the process that the gaseous refrigerant flows out of the compressor through the gas exhaust pipe 101, thereby reducing the lubricating oil flowing out along with the refrigerant and reducing the oil yield of the compressor. In this embodiment, the transition portion 302 is tapered, and in other embodiments, the transition portion may also be stepped or have other shapes, which is not limited in this application.

If the exhaust portion 303 is too short, the exhaust portion 303 cannot be fitted to the airtight plug during the factory inspection of the compressor, which affects the inspection of the airtightness. Therefore, the length of the exhaust portion 303 is L₃Then L in this embodiment₃And L satisfies 1/4<L₃:L<2/3. In one embodiment, L₃L can take the value of 0.3, 0.35, 0.4, 0.45, 0.5, 0.55, 0.6 or 0.65, etc. The exhaust unit 303 is used for connection to an external air conditioning system pipe or the like.

In this embodiment, through the experiment contrast on a model compressor, adopt the compressor of the blast pipe disclosed in this application to compare with prior art design, the performance of compressor under different operating conditions all has the improvement, all has the reduction at the oil circulation rate under different operating conditions. The detailed data are shown in table 1:

TABLE 1

As can be seen from table 1 above, in the compressor of this type, the performance of the compressor using the exhaust pipe disclosed in the present application is improved under the rotation speed conditions of 3600rpm, 4800rpm and 5400rpm, and the oil circulation rate is reduced.

In another embodiment of the present application, through experimental comparison on another model compressor, the compressor adopting the exhaust pipe disclosed in the present application has improved performance under most working conditions and reduced oil circulation rate under different working conditions compared with the prior art design. The detailed data are shown in table 2:

TABLE 2

As can be seen from table 1 above, in the compressor of this model, compared with the prior art, the performance of the compressor using the exhaust pipe disclosed in this application is not changed except that the performance of the compressor under the rotation speed condition of 3600rpm, and the performance of the compressor under the rotation speed conditions of 4800rpm, 5400rpm and 6000rpm is improved; in addition, the oil circulation rate is reduced under the conditions of different rotating speeds.

In another embodiment of the present application, as shown in fig. 5, the exhaust pipe 101 is tapered. In this embodiment, the first end portion 201 of the exhaust pipe 101 has an inner diameter larger than that of the second end portion 202. The shape of the exhaust pipe is not limited by the present application.

The embodiment of the utility model provides a still provide a compressor, this compressor includes above-mentioned arbitrary embodiment the blast pipe of compressor. The detailed structural features and advantages of the discharge pipe of the compressor can be referred to the description of the above embodiments, and will not be described herein.

To sum up, the utility model discloses an exhaust pipe and compressor of compressor have following advantage at least:

the inside diameter that the blast pipe is located the first end of casing through setting up the blast pipe of blast pipe and the compressor of this embodiment is greater than the inside diameter that the blast pipe is located the outer second end of casing, compare prior art when keeping second end internal diameter unchangeable, the inside diameter of blast pipe first end has been increased, the sectional area of gaseous circulation in the first end has been increased, gaseous refrigerant's velocity of flow has been reduced, and then the lubricating oil along with the refrigerant outflow has been reduced, rotor compressor's oil yield has been reduced, the operational reliability of compressor has not only been guaranteed, and the performance of compressor has been promoted.

In the description of the present invention, it is to be understood that the terms "bottom", "longitudinal", "lateral", "up", "down", "front", "back", "vertical", "horizontal", and the like, indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are used merely for convenience of description and simplification of description, but do not indicate or imply that the structures or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be construed as limiting the present invention. Furthermore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more and "several" means one or more unless otherwise specified.

In the description herein, references to the description of the terms "one embodiment," "some embodiments," "an illustrative embodiment," "an example," "a specific example," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

The foregoing is a more detailed description of the present invention, taken in conjunction with the specific preferred embodiments thereof, and it is not intended that the invention be limited to the specific embodiments shown and described. To the utility model belongs to the technical field of ordinary technical personnel, do not deviate from the utility model discloses under the prerequisite of design, can also make a plurality of simple deductions or replacement, all should regard as belonging to the utility model discloses a protection scope.

Claims

1. The exhaust pipe of the compressor is communicated with a shell of the compressor through an oil equalizing pipe, penetrates through an upper shell cover and is communicated with the inside of the shell, and is characterized in that the exhaust pipe is provided with a first end portion located in the shell and a second end portion located outside the shell, and the inner diameter of the first end portion is larger than that of the second end portion.

2. The discharge pipe of compressor as set forth in claim 1, wherein said compressor has a displacement Q and said first end portion has an inner diameter D₁Said D is₁And Q satisfies D₁:Q>1/6。

3. A discharge pipe of a compressor according to claim 1, wherein said discharge pipe has a flared portion, a transition portion, and a discharge portion in this order in a direction away from said shell; the inner diameter of the flared portion is equal to the inner diameter of the first end portion, and the inner diameter of the exhaust portion is equal to the inner diameter of the second end portion; the transition portion has an inner diameter that gradually decreases in a direction away from the housing.

4. A discharge pipe for a compressor as set forth in claim 3, wherein said discharge pipe is formed along a length extending direction of said discharge pipeThe length of the flaring part is L₁Said L is₁And L satisfies 1/5<L₁:L<2/3。

5. A discharge tube for a compressor as set forth in claim 3, wherein said discharge tube has a length L and said transition portion has a length L in a direction along which said discharge tube extends₂Said L is₂And L satisfies L₂:L<1/10。

6. A discharge pipe of a compressor as set forth in claim 3, wherein said discharge pipe has a length L and said discharge portion has a length L in a direction along which said discharge pipe extends₃Said L is₃And L satisfies 1/4<L₃:L<2/3。

7. A discharge pipe for a compressor as set forth in claim 3, wherein said flared portion is provided with an oil equalizing hole, and said oil equalizing pipe is communicated with said discharge pipe through said oil equalizing hole.

8. A discharge pipe for a compressor as set forth in claim 1, wherein an inner diameter of the first end portion of the discharge pipe has a value ranging from [16.1mm, 25mm ].

9. A discharge pipe of a compressor as set forth in claim 1, wherein said discharge pipe is tapered.

10. A compressor, characterized in that it comprises a discharge pipe of a compressor according to any one of claims 1 to 9.